Method for controlling the drive of a yarn winder, and the yarn winder thereof

ABSTRACT

A yarn winder in which a fluctuation of winding tension is avoided and the winding characteristics are made uniform from the most inner to the most outer layer. Yarn is wound by a winder in which a spindle 2 having a positively driven pressure roller 5 is positively driven, the pressure roller 5 being positioned so that it is not in contact with a tube 100 immediately after the yarn setting operation. After a predetermined amount of yarn layer has been wound on the tube 100, the pressure roller 5 is moved so that it contacts the yarn layer on the tube 100. The surface speed of the pressure roller 5 is controlled to be higher than that of an empty tube until the yarn is switched to the empty tube, wherein the controlled speed is approximately the same as or lower than the surface speed of a fully loaded tube, and the surface speed of the pressure roller is controlled to be approximately the same as the surface speed of the empty tube after the yarn has been switched to the empty tube.

This is a continuation of application Ser. No. 08/671,673 filed Jun. 28,1996; which is a continuation of application Ser. No. 08/209,910 filedMar. 14, 1994.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a yarn winder which winds a yarn at aspeed not less than 4000 m/min, and more particularly relates to acontrolling system for driving the yarn which can wind the yarn at highspeed.

2. Description of the Related Art

In general, when a yarn is wound after it has been spun out from aspinning machine, a winder is used which includes: a spindle to which atube is attached, wherein the spindle is rotatably mounted on a machineframe; a traverse unit disposed at an upper position of the spindle,wherein the traverse unit can be elevated in a vertical direction withrespect to the machine frame; and a pressure roller coming into contactwith a tube attached to the spindle so that a predetermined surfacepressure can be given to the tube.

In the case where the winding speed is not less than 6000 m/min, thespindle and pressure roller are positively rotated by a drive unit forpreventing the tube surface from being damaged when it is rubbed by thepressure roller, and also even in the case where the winding speed is4000 m/min to 6000 m/min, the spindle and pressure roller are positivelyrotated for improving a package configuration.

When the spindle rotating at the high speed described above is switchedfrom a fully loaded tube to an empty tube, the speed of the fully loadedtube is slightly increased and the winding tension is increased so thatthe yarn can be more strongly wound in yarn catching grooves formed onthe tube, and so that the yarn tension can be stabilized for preventingthe yarn from being wound around a godet roller disposed on the upstreamside of the winder.

However, in the case where the pressure roller is driven at apredetermined speed, a yarn on the upstream side of the winder is woundby the fully loaded tube after it has come into contact with thepressure roller. Therefore, when an increase of the speed of the fullyloaded tube is small, tension of the yarn on the upstream side of thewinder is not increased, so that the yarn is wound around the godetroller due to a decrease of tension when the yarn is switched. In thisway, the yarn switching operation fails. When the increase of the speedof the fully loaded tube is large, tension applied between the pressureroller and the fully loaded tube is greatly increased, so that the yarnis torn off when it comes into contact with the tube. In this way, theyarn switching operation also fails. Further, a problem is caused inwhich the yarn tension fluctuates in the case where the yarn is switchedso that the characteristics of the yarn wound in the most outside layerare changed.

In an ordinary yarn taking up operation, and yarn switching operation,including the yarn which is spun from a nozzle of a yarn spinningmachine, is directly wound on an empty tube rotated at a high speed, attime when the yarn is first set on the tube or when the yarn is firstswitched, the thickness of a yarn layer wound around the tube is verysmall. Therefore, when the pressure roller comes into contact with theyarn layer on the tube under the above condition, the yarn layer isbeaten and damaged by the pressure roller, which causes weaving specksin a weaving process and dyeing specks in a dyeing process.

In order to prevent the occurrence of the above problems in which theyarn layer is beaten and damaged by the pressure roller when thepressure roller comes into contact with the yarn layer on the tube underthe condition that the yarn layer on the tube is very thin, the pressureroller is provided with a step portion, and a pacer is provided at anend portion of a sliding shaft supporting the pressure roller so that agap can be formed between the pressure roller and the tube.

Further, the pressure roller described above is positively rotated by adrive unit, so that the pressure roller is not contacted with the yarnlayer when the yarn is set on the drum or when the yarn is switch orimmediately after the switch of the yarn. For this reason, it isimpossible to control the rotational speed of the spindle to which thetube is attached, in accordance with the rotational speed of thepressure roller.

Therefore, until the pressure roller comes into contact with the yarnlayer, the spindle speed is controlled by forward control based on thecalculation of a diameter of the yarn layer wound around the tubeutilizing a conventional manner. This forward control is switched tofeedback control in the following manner: When a yarn layer ofpredetermined thickness is formed on the tube, the yarn layer comes intocontact with the pressure roller so that the rotational speed (number ofrevolution) of the spindle is changed. Then the change in speed isdetected, and the rotational speed control of the spindle is switched tofeedback control in which the rotational speed of the spindle iscontrolled to a predetermined winding speed in accordance with therotational speed of the pressure roller.

According to a method in which the pressure roller is supported at apredetermined position and the yarn layer comes into contact with thepressure roller when a diameter of the yarn layer is increased as theyarn is wound around the tube, as illustrated in FIG. 17, it takes avery long period of time from a point of time (T1) when the yarn layeris formed on the tube and the yarn layer on the tube starts coming intocontact with the pressure roller, to a point of time (T3) when thesurface pressure is increased to a predetermined surface pressure (Pa).

Even when the yarn layer comes into contact with the pressure roller,the surface pressure varies according to the type, size and layerthickness of the yarn, and further the rotational condition of thepressure roller also varies.

For this reason, it is impossible to accurately detect the time at whichfeed forward control is switched to feedback control, and further thefollowing problems are caused:

Even when the surface pressure is not increased to the setting surfacepressure (Pa), feed forward control is switched to feedback control.Even after the surface pressure has increased to the predeterminedsurface pressure (Pa), feed forward control can not be switched tofeedback control. In this way, speed control can not be conductedaccurately, so that a difference is produced between the surface speedsof the yarn layer and the pressure roller. Accordingly, the yarn layeris affected.

In this case, the pressure roller is driven by an electric motorcontrolled by open loop control so that the rotational speed of thepressure roller can become a value corresponding to the setting speed.

When the spindle provided with a tube is rotated by the electric motorand the pressure roller comes into contact with the tube, winding of theyarn starts. Then the rotational speed of the pressure roller isdetected, and the electric motor for driving the spindle is subjected tofeedback control so that the pressure roller speed can be apredetermined value.

There is a slippage in the rotation of the electric motor itself, andfurther there is a rotational resistance in the rotation of the bearingportion of the electric motor, and also there is a rotational resistancein the rotation of the bearing portion of the roller. Accordingly, whenthe drive of the electric motor is controlled without givingconsideration to the slippage, the virtual rotational speed of thepressure roller is lowered with respect to the directed rotational speedof the electric motor. As a result, the pressure roller is driven by thespindle, so that an extra load is applied to a package, whichdeteriorates the configuration of the package.

Different from the above case, in a turret type winder in which theelectric motor for driving the pressure roller is subjected to open loopcontrol, when the pressure roller is not contacted with the package inthe case where the yarn is switched, the rotational speed of thepressure roller is not corrected even if the virtual rotational speed ofthe pressure roller is lowered with respect to the directed rotationalspeed. Consequently, the yarn winding tension is lowered.

When the yarn is switched from a fully loaded package to an emptypackage under the above condition, the yarn is wound around the rollersarranged on the upstream side of the winder, so that the success ratioof switching a yarn is lowered.

In order to solve the above problems, a slippage caused in the electricmotor for driving the pressure roller is measured after the completionof assembly of the winder in the manufacturing process, and the measuredslippage is converted into a correction coefficient, which is manuallyinputted into the control unit so as to be stored.

Further, the following winder is used when a yarn is wound after it hasbeen spun out from a spinning machine. The winder includes: a spindlerotatably attached to a machine frame, the spindle holding a pluralityof tubes; a pressure roller coming into contact with a yarn layer woundaround the tube held by the spindle; a traverse unit disposed on anupstream side of the pressure roller; a frame body to which the pressureroller is rotatably attached and also the traverse unit is integrallyattached, the frame body being supported by two guides provided in themachine frame in a cantilever condition so that the frame body can bevertically elevated; and a hydraulic cylinder supporting a portion ofthe frame body close to the cantilever portion. The winder having theabove construction is disclosed in the official gazette of JapaneseUtility Model Publication No. 57-57091.

Recently, in order to improve the winding capacity, the spindle lengthis increased so that the number of tubes to be held by the spindle canbe increased (the number is increased to 4 to 8). When the spindlelength is increased, the length of a pressure roller and that of atraverse unit are naturally increased.

However, a frame body to which the pressure roller and the traverse unitare attached is supported in a cantilever condition by two guidesprovided in the machine frame.

Therefore, as illustrated in FIG. 18, when the length from a gravitycenter (G) of the frame body 71 to the hydraulic cylinder 74 is L1, andthe weight of the frame body 71 and the pressure roller is W, the moment(W×L1) is applied to the sliding ball bearing 73 by which the frame body71 is slidably provided to the guide 72. For example, when the weight(W) of the frame body 71 and others is 200 Kg, and the length (L1) fromthe gravity center (G) of the frame body 71 to the hydraulic cylinder 74is 90 cm, the moment of 18000 Kg·cm is applied to the sliding ballbearing 73.

When the large moment described above is applied to the sliding ballbearing 73, the running resistance of the sliding ball bearing 73 isincreased, and the surface pressure of a pressure roller (not shown) cannot be correctly controlled, so that the configuration of a package isdeteriorated.

In order to allow it to receive such a high moment, the diameter andlength of the sliding ball bearing 73 are greatly increased. Therefore,the height of the frame body 71 on which the sliding ball bearing ismounted must be increased, so that the overall length of the winder isincreased.

In this connection, when a yarn is wound by the winder described above,since the spindle is mounted on the same machine frame as that of theframe body, vibration is transmitted to the frame body through themachine frame when the spindle is rotated. Further, since the pressureroller is contacted with the tube held by the spindle with apredetermined surface pressure, vibration of the spindle is transmittedto the frame body through the pressure roller.

Therefore, when the frequency of vibration caused by the rotation of thespindle winding a yarn coincides with the natural frequency of the framebody, the frame body resonates, so that the vibration is increased,which causes the collapse of the yarn layer of the package.

In the case where the winding operation is not conducted by the abovewinder, it is necessary to fix the pressure roller to the machine frameso that the pressure roller can not come into contact with the tube heldby the spindle under the condition that hydraulic fluid is not suppliedto a hydraulic cylinder. Therefore, as illustrated in FIG. 18, a stoppermeans 75 is provided at a position of the fore end of the frame body 71,wherein the position is located closer to the fore end than thecantilever supporting portion of the frame body 71.

The stopper means 75 is rotatably mounted on the machine frame 70, andcomposed of an engaging claw member 76 rotated by a hydraulic cylinder77, and an engaging piece 78 integrally attached to the frame body 71.When the engaging piece 78 is hooked at the engaging claw member 76, theframe body 71 is supported so that it can not be lowered.

Therefore, in the same manner as that of a case in which the frame body71 is supported by the hydraulic cylinder 74, when the length from thegravity center (G) of the frame body 71 to the hook position (G1) of thestopper means 75 is L1, and the length from the hook position (G1) ofthe stopper means 75 to the center of the guide 72 is L3, and the weightof the frame body 71 is W, the same moment (W×L1) as that applied to thesliding ball bearing 73 when the frame body 71 is supported by thehydraulic cylinder 74, is applied to the sliding ball bearing 73.

Therefore, a sliding ball bearing 73, the allowable moment of which ishigh, must be used for this device, so that the size of the frame body71 is increased in the height direction in the same manner as that ofthe case described above. Accordingly, an overall height of the winderis increased.

In this connection, Japanese Unexamined Utility Model Publication No.5-12454 discloses a construction in which guides are provided on bothsides of the frame body, and the frame body is elevated along the twoguides while both sides of the frame body are supported by the guides.

However, in order to elevate the long frame body in parallel withrespect to the spindle while both ends of the frame body are supportedby the guides, it is necessary to accurately machine the frame body andguides, and further predetermined rigidity is required for the framebody and guides.

Further, in order to maintain the pressure roller and spindle parallelwith each other without being affected by the condition of the floor onwhich the winder is installed, it is necessary to increase the sizes ofthe machine frame, guides and frame body.

In this connection, the construction of a drive type pressure roller isshown in FIG. 19, in which the pressure roller is positively rotated.The drive type pressure roller is constructed in the following manner:One shaft portion 81b of the roller 81 is rotatably provided in theframe body 95 for mounting the traverse head, through the bearingsection 82. The other shaft portion 81c is rotatably supported by thebearing section 87, and connected with the electric motor 89 through thecoupling 88. The bearing section 82 is composed of the bearing 83rotatably supporting the shaft portion 81b of the roller 81, and alsocomposed of the bracket 84 which is a supporting member of the bearing83. The bearing section 85 is composed of the bearing 86 rotatablysupporting the shaft portion 81c, and also composed for the bracket 87which is a supporting member of the bearing 86.

Alternatively, the construction of a drive type pressure roller is shownin FIG. 20, in which the drive type pressure roller is constructed inthe following manner: Both shaft portions 81b, 81c of the roller 81 arerotatably supported by the frame body 95 through the bearing 82. Oneshaft portion 81c is provided with the timing pulley 90, and the outputshaft of the electric motor 89 mounted on the frame body is providedwith the timing pulley 91. The timing belt 92 is provided between thetiming pulleys 90, 91. Rotation is transmitted to the roller 81 throughthe timing pulleys 90, 91 and the timing belt 92.

In the former case in which the electric motor is connected with theroller through the coupling, the size of the pressure roller mechanismof the longitudinal direction is increased. In the latter case in whichthe roller and the electric motor are disposed in parallel, the size ofthe pressure roller mechanism of the transverse direction is increased,and also the size of the height direction is increased, so that theoverall size of the winder is increased.

Further, the number of bearings is increased to a value of not less than4. Accordingly, when the winding operation is conducted at high speed ofnot less than 4000 m/min, energy loss is remarkably increased, and atthe same time an amount of heat generated by the electric motor isincreased, so that the lubricant of bearings assembled to the electricmotor is quickly deteriorated, and the bearing life is extremelyreduced. Further, in the high speed winding operation, the winding speedof which is 7000 m/min, the heat generated by the motor and bearing istransmitted to the roller body, so that the temperature of the rollerrises higher than the setting temperature. As a result, thecharacteristics of a yarn coming into contact with the roller body arechanged, and dyeing specks are caused in the latter process.

Next, an idle type pressure roller 80 rotated by a package is shown inFIG. 21, in which the shaft portions 81b are protruded onto both sidesof the roller body 81a, and this roller 81 is rotatably mounted on theframe body 13 through the bearing 82.

In the case where the pressure roller 80 is of the idle type, in thesame manner as that of the drive type, when a yarn is wound at a highspeed of not less than 4000 m/min, the bearing 83 of the bearing section82 is heated when the roller 81 is rotated at high speed by the tube orpackage tightly attached to the spindle 2. Therefore, the bracket 84coming into contact with an outer race portion of the bearing 83 isheated, and at the same time the shaft portion 81b coming into contactwith an inner race portion of the bearing 83 is also heated, so that thetemperature of end portions of the roller body 81a close to the shaftportion 81b is raised. However, since the bearing section is notforcibly cooled, the amount of heat radiated from the bearing 83 islarger than that radiated from the peripheral surface of the bracket 84.As a result, the lubricator in the bearing is quickly deteriorated, andthe life of the bearing 83 is reduced.

When the heat generated by the shaft portion 81b is only radiated fromthe peripheral surface of the end portion of the roller body 81a, thetemperature of the roller can not be immediately lowered, and furtherthe heat in the end portion of the roller body 81a is not transmitted tothe center of the roller body 81a. Accordingly, the temperature of theend portion of the roller body 81a becomes higher than the temperatureof the center. For this reason, the characteristics of the yarn cominginto contact with the portion of the roller, the temperature of which ishigh, are changed. As a result, dyeing and weaving specks are caused inthe process to which the yarn is subjected later.

In the present invention, the first problem to be solved, is describedas follows:

When the yarn is subjected to the switching operation, tension appliedto the yarn fluctuates. Therefore, the yarn is torn off and the yarnswitching operation fails, and further a package having uniformcharacteristics from the most inner to the most outer layer can not beprovided.

The second problem is described as follows:

It takes a long period of time from when the yarn layer provided on thetube comes into contact with the pressure roller, to when the surfacepressure is increased to a predetermined value. Further, it isimpossible to accurately detect the time at which feed forward controlis switched to feedback control.

The third problem is described as follows: The slippage characteristicsof an electric motor and the rotational resistance of a bearing aredifferent between the individual devices. Therefore, it is necessary tomeasure the slippage and to input a correction coefficient for eachwinder. Accordingly, it takes much time and labor. Since the correctioncoefficient is stored in a control unit, the correction coefficient mustbe inputted again each time a combination of the winder and control unitis changed.

The fourth problem is described as follows:

There is a difference between the temperature of the bearing at aninitial stage immediately after the start of the operation, and thetemperature of the bearing after it has operated over a long period oftime. Therefore, the rotational resistance differs, and the slippage ofthe electric motor is greatly changed. Further, when the rotationalresistance of the bearing is changed with age, the slippage of theelectric motor is also changed. Accordingly, a difference is causedbetween the previously measured and inputted slippage, and thesubstantial slippage. Therefore, the rotational speed of the pressureroller is lowered, and the pressure roller is rotated by a package. As aresult, a package of uniform configuration can not be provided.

The fifth problem is described as follows: When the rotational speed ofthe pressure roller is increased, the pressure roller drives thepackage, so that the electric motor is heated and may be damaged by anoverload.

The sixth problem is described as follows: In a turret type winder, yarnwinding tension fluctuates in the yarn switching operation. Therefore,the yarn is torn off or wound around other rollers, and a ratio ofsuccess is lowered in the yarn switching operation.

The seventh problem is described as follows: Since the frame body issupported in a cantilever condition, a high moment is applied to thesliding ball bearing, so that the running resistance of the sliding ballbearing is increased and the surface pressure of the pressure rollercannot be accurately controlled, which deteriorates the configuration ofa package.

The eighth problem is described as follows: When the frequency ofvibration caused by the rotation of the spindle in the yarn windingoperation coincides with the natural frequency of the frame body,resonance is caused in the winder, and the yarn layers of the packagecollapse.

The ninth problem is described as follows: When the frame body issupported by the stopper means, a high moment is applied to the slidingball bearing, so that a sliding bearing of high allowable moment must beused. As a result, an overall height of the winder is increased.

The tenth problem is described as follows: In a construction in whichthe drive electric motor is connected with the roller through acoupling, the size of the pressure roller mechanism of the longitudinaldirection is increased. In the case where the roller and drive electricmotor are provided in parallel, the size of the pressure rollermechanism of the transverse direction or the size of the heightdirection is increased. As a result, the overall size of the winder isincreased.

The eleventh problem is described as follows. The number of bearings isincreased to a value of not less than 4. Accordingly, when the spindleis rotated at a high speed of not less than 4000 m/min, energy loss isincreased, and at the same time an amount of heat generated by theelectric motor is generated. Therefore, the lubricant in the bearings inthe electric motor is quickly deteriorated, so that the life of thebearing is extremely reduced.

The twelfth problem is described as follows:

In the high speed winding operation in which a yarn is wound at a speedof 7000 m/sec, the heat generated by the electric motor and bearings istransmitted to the roller body. Therefore, the temperature is raised toa value higher than the setting temperature. Accordingly, thecharacteristics of a yarn coming into contact with the roller body arechanged, which causes dyeing and weaving specks in the later process.

SUMMARY OF THE INVENTION

The object of the present invention is to provide means for resolvingthe above-mentioned problems which are seemed to be drawbacks inconventional technologies.

In order to solve the first and second problems, according to a firstaspect of the present invention, there is provided a yarn winder havinga controlling means for controlling the drive of a yarn winder. In thewinder, when a yarn switching operation is carried out so that a yarn isdirectly wound on an empty tube, rotated by a spindle drive type winderhaving a positively driven pressure roller or a yarn is wound on anempty tube from a fully loaded tube, i.e., a tube on which yarn is fullywound thereon. And said controlling means is further provided with apositioning means for positioning the pressure roller so that thepressure roller is not contacted with a tube immediately after the yarnswitching operation when the yarn is switched to the empty tube; movingmeans for moving at least one of the pressure roller and the tube in adirection so that a distance between the pressure roller and the tube isreduced after a predetermined amount of yarn layer has been formed onthe tube to thereby permit the pressure roller to come into contact withthe yarn layer provided on the tube at a predetermined surface pressure;and means for controlling the surface speed of the pressure roller to behigher than that of the empty tube until the yarn is switched to theempty tube side.

Further, in the present invention, when the yarn is switched from theyarn-full-loaded tube to an empty tube, the yarn winder is furtherprovided with additional means for controlling the surface speed of thepressure roller so that the controlled speed of the pressure roller isapproximately the same as or lower than the surface speed of the fullyloaded the tube and after when the yarn is switched from theyarn-fully-loaded tube to the empty tube, the surface speed of thepressure roller is controlled so as to be approximately the same as thesurface speed of the empty tube.

According to a second aspect of the present invention, the presentinvention is to provide a means for controlling the drive of a yarnwinder in which a yarn is wound by a spindle drive type winder having apositively driven pressure roller, said method comprising the steps of;positioning the pressure roller so that the pressure roller is notcontacted with a tube immediately after the yarn setting operation oryarn switching operation; moving at least one of the pressure roller andthe tube in a direction so that a distance between the pressure rollerand the tube is reduced after a predetermined amount of yarn layer hasbeen formed on the tube; permitting the pressure roller to come intocontact with the yarn layer provided on the tube at a predeterminedsurface pressure; and switching the rotational speed control of thespindle from feed forward control based on the calculation of windingdiameter obtained by a conventional calculation method, to feedbackcontrol by which the rotational speed of the spindle is controlled to apredetermined winding speed based on the rotational speed of thepressure roller when the pressure roller comes into contact with theyarn layer formed on the tube.

In order to solve the third to sixth problems, according to a thirdaspect of the present invention, the present invention is to provide ameans for controlling the drive of the pressure roller of a yarn winderin which a yarn is wound by a spindle drive type winder having anelectric motor for driving the pressure roller, comprising the steps of:rotating the pressure roller by the electric motor at the yarn settingoperation or yarn switching operation under the condition that thepressure roller is not contacted with a tube tightly attached to thespindle; calculating a slippage caused in the electric motor; andcorrecting a command frequency given to the electric motor so as tocommand the rotation of the electric motor in accordance with theslippage.

Also, according to a fourth aspect of the present invention, the presentinvention is to provide a means for controlling the drive of thepressure roller of a yarn winder, further comprising the step ofcalculating the slippage caused in the electric motor for driving thepressure roller by the number of pressure roller rotation detectingpulses or the number of detected rotation when the pressure roller isrotated by the electric motor at a predetermined rotational speed, andalso calculated by the number of pulses or the number of rotation foundwhile the slippage of the electric motor is neglected. Alternatively,according to a fifth aspect of the present invention, the presentinvention is to provide a means for controlling the drive of thepressure roller of a yarn winder, further comprising the step ofcalculating the slippage caused in the electric motor for driving thepressure roller by a command frequency at the time when the pressureroller is rotated by the electric motor at a predetermined speed, andalso calculating by a frequency found while the slippage is neglected.

In order to solve the seventh problem, according to a sixth aspect ofthe present invention, the present invention is to provide a yarn windercomprising: hydraulic cylinders provided at both end portions of theframe body, wherein both end portions of the frame body are supported bythe two hydraulic cylinders.

According to a seventh aspect of the present invention, it is preferableto adopt the construction in which the inner diameters of the twohydraulic cylinders are different.

In order to solve the eighth problem, according to an eighth aspect ofthe present invention, the present invention is to provide a yarnwinder, in which a hydraulic fluid supply pipe is connected to eachhydraulic cylinder, and a control unit is provided and a pipe line ofthe hydraulic fluid supply pipe is changed or hydraulic pressure of thesupplied fluid is controlled in accordance with a signal sent from thecontrol unit.

In order to solve the ninth problem, according to a ninth aspect of thepresent invention, the present invention is to provide a yarn winder,comprising a stopper means for fixing the frame body to the machineframe so that the pressure roller is not contacted with the tubes heldby the spindle, the stopper means including a stopper member provided onthe machine frame side and an engaging member provided in the framebody, wherein a contact surface of the stopper and engaging members isinclined by and angle of 0° to 45° so that a lower tangential line ofthe contact surface is inclined toward the cantilever supporting side ofa movable frame body.

In order to solve the tenth problem, according to a tenth aspect of thepresent invention, the pressure roller of the yarn winder comprises anelectric motor provided at one end portion of the pressure roller,wherein a shaft of the pressure roller and an output shaft of theelectric motor are commonly used. According to an eleventh aspect of thepresent invention, the pressure roller of the yarn winder compriseselectric motors provided at both end portions of the pressure roller,wherein a shaft of the pressure roller and an output shaft of theelectric motor are commonly used.

In order to solve the eleventh and twelfth problems, according to atwelfth aspect of the present invention, the present invention is toprovide a pressure roller of the yarn winder comprising an electricmotor provided at one end portion of the pressure roller, wherein ashaft of the pressure roller and an output shaft of the electric motorare commonly used, and a heat conductive member is inserted into ahousing portion of the electric motor in such a manner that the heatconductive member is protruded onto the opposite side to the pressureroller and a cooling member is attached to the protruding portion of theheat conductive member. According to other embodiment of this aspect,the present invention is to provide a pressure roller of the yarn winderin which the heat conductive member is inserted into a core portion ofthe pressure roller in the longitudinal direction of the core includingat least the housing portion of the electric motor. According to anotherembodiment of this aspect, the present invention is to provide apressure roller of the yarn winder in which the pressure roller isrotatably attached to a supporting member through a bearing, and a heatconductive member is inserted into the pressure roller in thelongitudinal direction of the core of the pressure roller including atleast bearing portions provided at both ends.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view showing an example of an overallarrangement of the spindle drive type winder for realizing the methodfor controlling the drive of a yarn winder of the present invention.

FIG. 2 is a schematic illustration showing an example of theconstruction of the supporting portion of the traverse unit shown inFIG. 1.

FIG. 3 is a schematic illustration showing a condition of the surfacepressure applied when the pressure roller of the winder of the presentinvention is contacted with the yarn layer provided on the tube.

FIG. 4 is a plan view showing an outline of an example of the yarnwinder of the present invention.

FIG. 5 is a view taken on line I--I in FIG. 4.

FIG. 6 is an enlarged view showing the portion II outline in FIG. 5.

FIG. 7 is a view taken on line III--III in FIG. 6.

FIG. 8 is a schematic illustration showing the first example of thehydraulic fluid supply pipe connected with the hydraulic cylinder shownin FIG. 4.

FIG. 9 is a schematic illustration showing the second example of thehydraulic fluid supply pipe connected with the hydraulic cylinder shownin FIG. 4.

FIG. 10 is a schematic illustration showing the third example of thehydraulic fluid supply pipe connected with the hydraulic cylinder shownin FIG. 4.

FIG. 11 is a sectional view showing an outline of the first example ofthe construction of the pressure roller of the winder of the presentinvention.

FIG. 12 is a sectional view showing an outline of the second example ofthe construction of the pressure roller of the winder of the presentinvention.

FIG. 13 is a sectional view showing an outline of the third example ofthe construction of the pressure roller of the winder of the presentinvention.

FIG. 14 is an end view of the stator mounting portion of the motor ofthe winder.

FIG. 15 is a sectional view showing an outline of the fourth example ofthe construction of the pressure roller of the winder of the presentinvention.

FIG. 16 is a sectional view showing an outline of the fifth example ofthe construction of the pressure roller of the winder of the presentinvention.

FIG. 17 is a schematic illustration showing a condition of surfacepressure in the case where the pressure roller is contacted with a yarnlayer on the tube of the conventional winder.

FIG. 18 is a schematic illustration showing an example of the stoppermeans of the conventional winder.

FIG. 19 is a schematic illustration showing an example of the idle typepressure roller of the conventional winder.

FIG. 20 is a schematic illustration showing the first example of thepressure roller of the conventional winder.

FIG. 21 is a schematic illustration showing the second example of thepressure roller of the conventional winder.

FIGS. 22 to 25 show flowcharts indicating sequences of operations forcontrolling the drive of the yarn winder of the present invention.

FIG. 26 shows a schematic view of another embodiment of the hydraulicfluid supply pipe.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

A specific embodiment of the yarn winder of the present invention willbe explained with reference to the attached figures, hereunder.

FIG. 1 shows a schematic view of a construction of one specificembodiment of the yarn winder concerning the present invention and alsoshows a drive controlling means to realize the controlling method forcontrolling the driving system of the yarn winder of the presentinvention.

Note that, FIG. 1 shows one embodiment of the yarn winder of the presentinvention. And the yarn winder in which a yarn 200 is wound on a tube100 fixedly coupled with a spindle 2 provided in a spindle drive typewinder having a positively driven pressure roller 5, wherein,immediately after when a yarn 200 is taken up on an rotating tube 100 ata period of a yarn switching operation, the pressure roller 5 isarranged to be set at a position so as to be separated from a surface ofsaid tube 100 with a predetermined distance L interposed therebetweenwhereby not to contact with a tube 100 and after when a predeterminedamount of yarn layer has been formed on the tube 100, at least one ofthe pressure roller 5 and the tube 100 is moved in a direction so thatsaid predetermined distance L formed between the pressure roller 5 andthe tube 100, is reduced, and thereafter said pressure roller 5 ispermitted to come into contact with a surface of the yarn layer 220provided on the tube 100 at a predetermined surface pressure.

In the above-mentioned yarn winder, the yarn switching operationincludes a case in which the yarn 200 supplied from a yarn supply meansis directly wound on an empty yarn tube 100 and a case in which the yarn200, supplied from a yarn supply means and already wound on the tube toform a fully loaded tube 215, is switched from the fully loaded tube 215to an empty tube 100.

The detailed explanation concerning the yarn winder of the presentinvention which has the above-mentioned basic technical features, willbe explained with reference to FIGS. 1 to 3, hereunder.

FIG. 1 is a perspective view showing an example of an overallarrangement of the spindle drive type winder for realizing the methodfor controlling the drive of a yarn winder of the present invention. Thewinder includes: an electric motor 3 for driving; a spindle 2 fortightening a tube, rotatably provided in a machine frame 1; a traverseunit 4 provided at an upper position of the spindle 2, wherein thetraverse unit 4 is vertically elevated along a guide (not shown) formedin the machine frame 1; and an electric motor 6 for driving. The winderfurther includes: a pressure roller 5 rotatably provided in the traverseunit 4; a first detector 7 for detecting the rotational speed of thespindle, provided at the rear of the electric motor 3; a second detector8 for detecting the rotational speed of the pressure roller, providedclose to an output shaft of the electric motor 6; and a control unit 9for controlling the rotational speed of each electric motor.

The first and second detectors 7, 8 described above use a pulse pickupof the optical, magnetic and proximity types.

The control unit 9 uses a microcomputer having the functions ofinputting, storing, comparative calculation and operation command.

The traverse unit 4 includes: a slider 12 engaged with a guide 1a formedin the machine frame 1, the slider 12 being elevated in a verticaldirection; a frame body 13 disposed in an upper position of the spindle2, being attached to the slider 12 in parallel with the spindle 2; and adrive mechanism (not shown) of traverse units 14-1, 14-2 attached to theframe body 13 so that a predetermined interval can be provided in thesame direction as the longitudinal direction of the spindle 2.

The traverse units 14-1, 14-2 described above are constructed in thefollowing manner: A plurality of impellers are mounted on a plurality ofrotational shafts, and the impellers are rotated together with therotational shafts, so that a reciprocating motion can be given to ayarn.

Alternatively, the traverse units 14-1, 14-2 described above areconstructed in the following manner: A traverse guide is engaged with agroove formed on the peripheral surface of a rotational roller, and thetraverse guide is reciprocated in the longitudinal direction of the axisof the spindle 2, so that the yarn can be traversed.

The aforementioned surface pressure giving mechanism 10 includes asshown in FIG. 2: a piston 15, the head 15a of which is movably insertedinto an air chamber 12a formed in the slider 12 so as to move along alongitudinal direction of the chamber 12a, the lower end of which isfixed to the machine frame 1 through a bracket 16; an electromagneticchangeover valve 17a; a pressure regulating valve (not shown); and afluid supply pipe 17 for supplying hydraulic fluid such as compressedair, connected with the air chamber 12a of the slider 12.

Instead of the above cylinder mechanism of the slider 12 composed of theair chamber 12 and piston 15, a hydraulic cylinder or a pneumaticcylinder available in the market may be used. In this respect, the term"hydraulic" is used herein in a generic sense to mean cylinders actuatedby fluids including not only liquid actuating fluids, as implied byhydraulic, but also gaseous actuating fluids such as compressed air.

When fluid of high pressure is supplied to the air chamber 12a, thepressure roller 5 attached to the frame body 13 is raised together withthe slider 12, so that the surface pressure impressed upon the spindle 2is reduced, and when fluid of low pressure is supplied to the airchamber 12a, the surface pressure is increased.

The above support mechanism 11 is composed of a hydraulic cylinder 18attached to the slider 12, and a fluid supply pipe 19 having anelectromagnetic changeover valve 19a.

In the yarn setting operation, or in the yarn switching operation,hydraulic fluid is supplied to the hydraulic cylinder 18, so that thepiston rod 18a is protruded and the frame body 13 is raised togetherwith the slider 12. In this way, a predetermined gap is formed betweenthe pressure roller and the tube 100 mounted on the spindle 2. When theyarn setting operation or the yarn switching operation is completed, atimer or a winding diameter detecting sensor detects that apredetermined amount of yarn layer 220 has been formed around the tube100, and then a fluid supply stop signal is sent from the control unit 9to the fluid supply pipe 19 of the support mechanism 11 for the tube100. Then the piston rod 18a of the hydraulic cylinder 18 is withdrawnand the pressure roller 5 comes into contact with the yarn layer formedon the tube 100. Simultaneously when the operation signal is sent to thefluid supply pipe 19, or after a predetermined period of time haspassed, the rotational speed control of the spindle 2 is switched fromfeed forward control to feedback control in which the rotational speedof the spindle 2 is controlled in accordance with the rotational speedof the pressure roller so that the rotational speed of the spindle 2 canbe a predetermined winding speed.

A rotary encoder or a pulse detector to detect teeth or holes with achange in light, magnetic force or electrostatic capacity, may be usedfor the first detector 7 for detecting the rotational speed of theelectric motor 3, and for the second detector 8 for detecting therotational speed of the pressure roller 5.

It is not necessary to provide a step portion onto the pressure roller 5for preventing the yarn layer 220 formed on the tube 100 from cominginto contact with the pressure roller 5.

The drive control operation of the above winder will be explained asfollows.

First, the yarn winding speed, traverse speed, number of traverse,winding surface pressure, yarn winding amount, and yarn layer formingtime are inputted into the control unit 9.

Next, the electromagnetic changeover valve 19a of the fluid supply pipe19 is operated, so that the pipe line is changed over and fluid at apredetermined pressure is supplied to the hydraulic cylinder 18. Thenthe piston rod 18a is protruded, and the frame body 13 is raisedtogether with the slider 12, and a predetermined gap L is formed betweenthe pressure roller 5 and the tube 100 attached to the spindle 2.

When fluid of a predetermined pressure is supplied from the fluid supplypipe 17 to the air chamber 12a of the slider 12, the pressure roller 5can be contacted with the tube 100 attached to the spindle 2 with apredetermined surface pressure.

After these preparations have been made, the rotational speed of thespindle 2 and that of the pressure roller 5 are controlled to apredetermined yarn winding speed in accordance with the speed commandsignal sent from the control unit 9. Then a yarn 200 is wound around thetube 100 attached to the spindle 2 by the action of a yarn settingmechanism (not shown), so that a yarn layer 220 (the winding thickness:0.1 to 0.4 mm) is formed. Simultaneously when the yarn is wound aroundthe tube 100, the winding diameter calculating means (not shown)provided in the control unit 9 is operated, and the winding diameter iscalculated by a predetermined winding condition and the rotational speedof the spindle 2. When the winding diameter is increased to apredetermined value, a pipe line switching operation signal is sent fromthe control unit 9 to the electromagnetic changeover valve 19a of thefluid supply pipe 19 in the support mechanism 11. Therefore, the pipeline is switched, and the supply of fluid to the hydraulic cylinder 18is stopped.

Then the piston rod 18a of the hydraulic cylinder 18 is withdrawn, theframe body 13 is lowered together with the slider 12, and the pressureroller 5 comes into contact with the yarn layer formed on the tube 100.As illustrated in FIG. 3, a period of time from when the pressure roller5 starts coming into contact with the yarn layer on the tube 100 (T1),to when the pressure surface is increased to a predetermined value Pa(T2), is very short.

Simultaneously when the operation signal is sent to the fluid supplypipe 19 of the support mechanism 11, or after a predetermined period oftime has passed, the rotational speed control of the spindle 2 isswitched by the control unit 9 from feed forward control in whichcontrol is conducted in accordance with the winding diametercalculation, to feedback control in which the rotational speed of thespindle 2 is controlled in accordance with the rotational speed of thepressure roller 5 so that the rotational speed of the spindle 2 canbecome a predetermined winding speed.

Then the rotational speed of the pressure roller 5 detected by thesecond detector 8 is sent to the control unit 9, and the rotationalspeed of the spindle 2 is subjected to feedback control so that it canbe a predetermined winding speed.

As described above, simultaneously when the yarn setting operation hasbeen completed, the winding diameter calculating means (not shown) isoperated and the amount of formed yarn layer is calculated. When thecalculated value becomes a predetermined one, the hydraulic cylinder ofthe support mechanism 11 is operated so that the pressure roller 5 canbe forcibly contacted with the yarn layer formed on the tube 100, and atthe same time the rotational speed control of the spindle 2 is switchedfrom forward control to feed back control. Therefore, the rotationalspeed control of the spindle 2 can be switched at a constant timedrelation. At the same time, the rotational speed control of the spindle2 is switched under the condition that the pressure roller 5 iscontacted with the yarn layer on the tube 100 with a predeterminedsurface pressure. Accordingly, speed control can be accuratelyperformed.

Instead of the above winder having a single spindle, in the case where aturret type winder, as shown in FIG. 5, is used, in which a plurality ofspindles are rotatably attached to the turret member so as to wind ayarn, the operation is conducted in the following manner. When the yarnsetting operation is completed by the yarn setting mechanism (notshown), or when a fully loaded tube 215 is switched to an empty tube 100by the yarn switching mechanism (not shown), the winding diametercalculating means (not shown) is operated and the amount of formed yarnlayer 220 is calculated. Then the pressure roller 5 is forciblycontacted with the yarn layer 220 formed on the tube 100, and at thesame time, the surface speed of the pressure roller 5 is controlled tobe higher than that of the empty tube 100 until the yarn 200 is switchedto the empty tube side, wherein the controlled speed is approximatelythe same as or lower than the surface speed of the fully loaded tube215, and the surface speed of the pressure roller 5 is controlled to beapproximately the same as the surface speed of the yarn layer 220 formedon the empty tube 100 after the yarn has been switched to the emptytube. When speed control is conducted in the above manner, fluctuationof tension can be avoided in the yarn switching operation, and the yarncan be switched from the fully loaded tube to the empty tube while theyarn is not torn off or the yarn is not wound around the pressure roller5.

When the speed of the pressure roller 5 is switched at least before theyarn starts traversing, the characteristics of the yarn wound around thetube can be made uniform from the most inner to the most outer layer.

In the above winder, a slippage is caused in the electric motor fordriving the pressure roller when the pressure roller 5 is rotated. Theslippage caused in the case where the winder is stopped over a longperiod of time and the bearing temperature is low, is different from theslippage caused in the case where the winder has been operated for apredetermined period of time and the bearing temperature is high.

Therefore, it is necessary to calculate the slippage at least before thepressure roller 5 comes into contact with the winding package such as anempty tube 100, in the yarn setting and yarn switching operation. In thecase of the manual yarn switching type winder shown in FIG. 1, it isnecessary to calculate the slippage before the completion of yarnsetting operation after the start of the winder, or before thecompletion of yarn setting operation after the fully loaded tube wasreplaced with the empty tube after the completion of winding. In thecase of the turret type winder, it is preferable that the yarn settingoperation for the start of winding is completed. That is, it ispreferable that the slippage is calculated before the yarn is switchedfrom the fully loaded tube to the empty tube after the completion ofwinding.

In this connection, in order to improve the success ratios of yarnsetting and yarn switching, the rotational speed of the spindle is setto be a little higher than the winding speed in the case of yarn settingor yarn switching. After the completion of yarn setting or yarnswitching, the rotational speed of the spindle is reduced to apredetermined winding speed.

Therefore, the slippage caused in the electric motor 6 when it drivesthe pressure roller 5 in the first yarn setting operation and the firstyarn switching operation, is calculated under the condition that thewinder is operated at the yarn setting speed or the yarn switching speedand further the pressure roller 5 is not contacted with the spindle 2.

First, the calculation method for calculating a slippage will beexplained as follows.

The first yarn setting operation is taken for an example. When the yarnsetting speed is SI (m/min), the diameter of the pressure roller 5 is DR(m), and the number of poles of the electric motor 6 is p1, the commandfrequency RO1 (Hz) is expressed as follows when the slippage isneglected. ##EQU1##

When the number of pulses per one revolution of the pressure roller isP1, the number of pulses RFP1 (pulse/sec) corresponding to the yarnsetting speed SI of the pressure roller can be calculated by thefollowing expression. ##EQU2## When the number of rotation detectingpulses of the pressure roller is RFP2 (pulse/sec), the slippage ηF canbe calculated by the following expression. ##EQU3##

After substitution of RFP1 from the above expression (2) to theexpression (3), slippage ηF can be calculated from the command frequencyRO1 (Hz) and the number of pressure roller rotational detecting pulsesRFP2 (pulse/sec). The expression is shown as follows. ##EQU4## On theother hand, when the package diameter is DM (m) and the number of polesof the electric motor 3 for driving the spindle is p2, the commandfrequency SF1 (Hz) of the electric motor 3 is expressed as follows.##EQU5##

When the number of pulses per one revolution of the spindle is P2, thenumber SFP1 (pulse/sec) of pulses corresponding to the yarn settingspeed of the spindle is calculated by the following expression. ##EQU6##

The pressure roller drive control operation of the above manual yarnswitching type winder will be explained as follows.

First, an operation switch (not shown) is pressed so that the traversehead 4 is lowered. When the pressure roller 5 is stopped at a slippagemeasuring position separate from the spindle 2 by a predetermineddistance, the electric motor 3 for driving the spindle and the electricmotor 6 for driving the pressure roller are activated, so that thespindle 2 and pressure roller 5 are rotated.

At this time, in order to maintain a predetermined speed, feedbackcontrol is conducted on the electric motor 3 so that the number ofpulses of the output shaft of the electric motor 3 for driving thespindle, the pulses being sent from the first detector 7, can becomeequal to the number SFP1 (pulse/sec) of pulses corresponding to the yarnsetting speed SI, wherein the number SFP1 (pulse/sec) of pulses iscalculated by the above expression (6).

In this connection, the electric motor 6 for driving the pressure rolleris driven in accordance with the command frequency RO1 (Hz) found by theexpression (1).

Under this condition, the number RFP2 (pulse/sec) of pressure rollerrotation detecting pulses of the pressure roller 5 is detected by thesecond detector 8 and sent to the control unit 9. Then the slippage ηFis calculated by the expression (4) and stored in the control unit 9.

Then the correction command frequency RF1 (Hz) given to the electricmotor 6 for driving the pressure roller at the yarn setting speed SI(m/min) is calculated by the following expression (7) to which theslippage ηF is added. ##EQU7##

When the electric motor 6 is subjected to open loop control by the abovecorrection command frequency RF1 (Hz) and the pressure roller 5 isrotated, the yarn is set around the tube attached to the spindle 2.

After the yarn has been set around the tube, the winding operationstarts. Then the electric motor 6 for driving the pressure roller issubjected to open loop control by the command pressure roller frequencyOM (Hz) obtained from the following expression (8).

When the steady winding speed is SM (m/min), the command pressure rollerfrequency OM (Hz) is calculated by the following expression. ##EQU8##

In this connection, the electric motor 3 for driving the spindle issubjected to feedback control so that the number of pulses of the outputshaft of the electric motor 3 sent from the first detector 7 can beequal to the number of pulses SMP (pulse/sec) corresponding to thesteady winding speed SM of the spindle calculated by the followingexpression (9). ##EQU9##

In the above expression (9), DM is a package diameter (m), which is thesame as the tube diameter at the start of yarn winding operation.

In this case, the package diameter DM (m) is calculated by the followingexpression (10) ##EQU10## where the winding time is T (min), the amountof discharged polymer spun out from a spinning machine (not shown) is L(g/min), the yarn winding width is W (m), the package density is ρ(g/m³), and the tube diameter is DS (m).

In accordance with the value calculated by the above expression, theyarn 200 is wound so that the yarn layer 200 is formed on the tube 100.Then, the outer peripheral portion of the yarn layer comes into contactwith the pressure roller 5, so that a steady winding condition isprovided. Then the electric motor 3 for driving the spindle is subjectedto feedback control so that the number of pulses of pressure rollerrevolution detection can be coincident with the number of pulses RPM(Hz) corresponding to the steady winding speed SM of the pressureroller. The number of pulses RPM (Hz) corresponding to the steadywinding speed SM of the pressure roller is calculated by the followingexpression. ##EQU11##

In the case where the yarn 200 is wound under the condition ofoverfeeding, the command pressure roller frequency OS (Hz) is calculatedby the following expression, wherein the overfeeding ratio is F%.##EQU12##

In general, it is sufficient that the above overfeeding ratio is 0 fromthe start to the end of winding, or the above overfeeding ratio is setto be a constant value. However, for the purpose of improving theconfiguration of a package, it is possible to define the overfeedingratio as a function of the winding diameter or the winding time.

In the manual operation type winder shown in FIG. 1, after apredetermined amount of yarn has been wound, the yarn is cut off, andthe fully loaded package is replaced with an empty tube so as to conductthe yarn setting operation.

The aforementioned winder is continuously operated for a predeterminedperiod of time. Therefore, the temperatures of bearings and others areraised, so that the slippage is varied.

Accordingly, before the start of yarn setting operation, the slippage ofthe pressure roller 5 is calculated in the same manner as that of thefirst yarn setting operation.

In the manual switching type winder, the above calculation forcalculating the slippage is conducted for each yarn setting operation.It is also possible to conduct the calculation every other yarn windingoperation.

Next, calculation of slippage in the turret type winder, as shown inFIG. 5, will be explained as follows.

When a turret type winder is used, in which a plurality of spindles 2,2' are attached to the turret member 20, the winding operation isconducted in such a manner that a yarn 200 is successively switched froma spindle 2 having a fully loaded tube 215 to a spindle 2' having anempty tube 100. In this case, slippage is calculated in the followingmanner: At the first yarn setting operation, and also before a fullyloaded tube around which a predetermined amount of yarn has been woundis switched to an empty tube, under the condition that the pressureroller 5 is not contacted with the spindle 2, slippage between thebearing of the pressure roller 5 and the electric motor 6 is calculatedfrom the command frequency with respect to the yarn switching speed ofthe electric motor 6 for driving the pressure roller, and also from thenumber of pressure roller revolution detecting pulses.

Slippage in the above turret type winder as shown in FIG. 5, iscalculated in the following manner:

The yarn setting speed SI (m/min) in the above expression (1) issubstituted by the yarn switching speed SH (m/min). Then the commandfrequency (Hz) for the electric motor 6, and the number of pulses(pulse/sec) corresponding to the pressure roller yarn switching speedSH, are calculated, and then slippage is calculated by the slippagecalculating expression.

That is, when the slippage is neglected, the command frequency RH1 (Hz)is expressed by the following expression. ##EQU13##

The number of pressure roller feedback pulses RFHP1 (pulse/sec) iscalculated by the following expression. ##EQU14## When the number ofpressure roller rotation detecting pulses is RFHP2 (pulse/sec), slippageηH is calculated by the following expression. ##EQU15##

When RFHP1 in the above expression (14) is substituted by RFP1 in theexpression (15), slippage ηH can be calculated from the commandfrequency RH1 (Hz) and the number of pressure roller rotation detectingpulses RFHP2 (pulse/sec). The expression is described as follows.##EQU16##

In the turret type winder, the above calculation for calculating theslippage is conducted at the first yarn setting operation and at thetime of each yarn setting operation. However, it is also possible toconduct the calculation every other yarn winding operation.

In the above example, slippage is calculated when the rotational speedof the pressure roller 5 is detected as the number of pulses, however,slippage can be also calculated when the rotational speed is detected bya tachometer type generator as the number of revolution.

As described in the above example, when slippage is calculated, theelectric motor 6 for driving the pressure roller 5 is controlled inaccordance with the command frequency calculated by the expression (1)in which slippage is neglected or the expression (13), and afterslippage has been calculated, the electric motor 6 for driving thepressure roller is controlled in accordance with the slippage correctedby the calculated slippage. Therefore, the number of revolution of thepressure roller is changed by the amount of slippage.

In order to reduce a change in the number of revolution of the pressureroller, the amount of slippage calculated before is added to the yarnsetting value SI in the expression (1) or the yarns switching speed SHin the expression (13).

The aforementioned slippages ηF and ηH are calculated in accordance withthe command frequency of the electric motor 6 for driving the pressureroller, and the number of pressure roller rotation detecting pulses, orthe slippages ηF and ηH are calculated in accordance with the number ofpressure roller rotation detecting pulses, and the number of pulsescorresponding to the pressure roller yarn setting speed or yarnswitching speed calculated while the slippage is neglected. However, theslippages ηF and ηH can be calculated in the following manner:

The rotational speed or frequency is substituted in the above expressionof the number of pulses, and the slippage can be found from the pressureroller detecting rotational speed in the case where the pressure rolleris rotated by the electric motor, and also from the rotational speedcalculated when slippage is neglected, and also the slippage can befound from the command frequency in the case where the pressure rolleris rotated by the electric motor, and also from the frequency calculatedwhile slippage is neglected.

Of course, the above drive control method can be applied to a turrettype winder in which a plurality of spindles are attached to the turretmember.

Next, the construction of the yarn winder of the present invention willbe explained as follows.

FIG. 4 is a plan view showing an outline of an example of the yarnwinder of the present invention. FIG. 5 is a view taken on line I--I inFIG. 4. FIG. 6 is an enlarged view showing an outline of the portion IIin FIG. 5. FIG. 7 is a view taken on line III--III in FIG. 6. The winderincludes: a turret member 20 rotatably provided in the machine frame 1;two spindles 2, 2' rotatably provided in the turret member 20 forsupporting a plurality of tubes 100; a slider 12 mounted in a cantilevermanner on the two guides 1a provided in the machine frame 1, a slidingball bearing 21 being used so that the slider 12 can be verticallyelevated; a frame body 13 integrally attached to the slider 12; atraverse unit 4; a pressure roller 5 rotatably attached to the framebody 13 through a bearing (not shown in the drawing); a traverse unit 14integrally attached to the frame body 13 so that the traverse unit 14can be positioned in the upstream of the pressure roller 5; a firsthydraulic cylinder 22 for supporting the slider, the first hydrauliccylinder 22 being disposed close to the guide 1a; a second hydrauliccylinder 23 for supporting the frame body, the second hydraulic cylinder23 being disposed at a fore end portion of the frame body 13; a stoppermeans 24 provided in the machine frame 1 so that the stopper means 24can be positioned above the first hydraulic cylinder 22; a hydraulicfluid supply pipe 25 connected with the hydraulic cylinders 22, 23; anda control unit 9 for controlling the rotation of the spindle 2 and alsocontrolling the supply of hydraulic fluid to the hydraulic cylinders 22,23.

It is possible to attach the traverse unit 4 to the frame body 13, andit is also possible to rotatably attach the pressure roller to thetraverse unit 4.

The pressure roller 5 is provided with an electric motor for driving, oralternatively the pressure roller 5 is driven by the spindle 2.

The aforementioned slider 12 and frame body 13 are composed of twomembers, however, they may be formed into an integrated frame body fromone member, or the machine frame of the traverse unit may be formed intothe frame body.

A vibration detector 26 is mounted on an upper fore end portion of theframe body 13, and a detected oscillation value is sent to the controlunit 9.

The turret member 20 is rotatably attached to the machine frame 1through a bearing 27. By the action of a drive unit (not shown), onespindle 2 is rotated from a winding position to a waiting position, andthe other spindle 2 is rotated from the waiting position to the windingposition.

The spindle 2 is rotatably attached to the turret member 20 through abearing (not shown), and rotated by the electric motor 28 connected withan end portion of the spindle 2.

The following constructions are used for the traverse unit 4:

One is a construction in which a cam shoe to which a yarn guide isintegrally attached is engaged with a groove of a scroll cam roller, andwhen the scroll cam roller is rotated, the cam shoe is reciprocated, sothat a yarn can be traversed. The other is a construction in which ayarn is traversed by a rotational body having a plurality of impellers.

Single acting cylinders are used for the hydraulic cylinders 22, 23. Thecylinder bodies 22a, 23a are fixed to the predetermined positions of theslider 22 and frame body 13 with screws (not shown) so that the pistonrods 22b, 23b can be positioned downward, and end portions of the pistonrods 22b, 23b are attached to the machine frame 1 through sphericalbearings 29, 30.

The above hydraulic cylinders 22, 23 are disposed in the followingmanner:

The axis of each hydraulic cylinder is vertically disposed beingperpendicular to the axis of the pressure roller 5, and the hydrauliccylinders 22, 23 are disposed at a predetermined interval on a linepassing through the gravity center G of the frame body 13, pressureroller 5 and traverse unit 4 in parallel with the axis of the pressureroller 5.

However, consideration must be given to the setting position of thehydraulic cylinder 23 at which interference can be avoided in themovement of a fully loaded package from the winding position to thewaiting position and also interference can be avoided in the liftingmotion of the fully loaded package. Also, consideration must be given tothe adjustment of the setting positions of the hydraulic cylinders 22,23 so that the setting positions can be easily adjusted with respect tothe position of gravity center G. Therefore, as shown in FIG. 4, it ispreferable that the hydraulic cylinders 22, 23 are disposed in thefollowing manner: The axis of each cylinder is vertical andperpendicular to the axis of the pressure roller 5, and the hydrauliccylinders are disposed in the horizontal direction perpendicular to thelongitudinal direction of the axis of the pressure roller 5 so that thehydraulic cylinders are positioned on the line passing through thegravity center position G of the frame body 13, pressure roller 5 andtraverse unit 4.

As illustrated in FIGS. 6, 7, the stopper means 24 includes: a mountingmember 31 mounted on the machine frame 1 with bolts 32; a stopper member33 rotatably attached to the mounting member 31 with a pin 34; ahydraulic cylinder 35 for rotating the stopper member 33; and anengaging member 36 attached to the slider 12 with bolts 37.

The cylinder 35 is connected with a supply pipe 53 having anelectromagnetic valve 52 for supplying actuating fluid such ascompressed air.

When the piston rod of the hydraulic cylinder 35 is protruded under thecondition that the engaging member 36 is pushed upward together with theslider 12 by the hydraulic cylinders 22, 23, the stopper member 33 isrotated counterclockwise and moved to the waiting position, so that theengaging member 36 can be moved downward.

It is necessary that a contact surface between the stopper member 33 andthe engaging member 36 is formed in the following manner:

A lower tangential line of the contact surface is inclined toward thecantilever supporting side of the slider 12 with an angle larger than 0°and smaller than 45° with respect to the vertical line, so that acomponent force W2 generated on the contact surface can offset a momentactivated on the sliding ball bearing 21.

The inclination angle θ is set in an angular range from an angle atwhich a moment generated by the angle θ becomes lower than an allowablemoment of the sliding ball bearing 21, to an angle at which the engagingmember 36 can be positively supported by the stopper member 33irrespective of the rigidity and error caused in the machining andassembling processes of the stopper member 33 and engaging member 36 ofthe stopper means 24.

When the contact surface of the engaging member 36 is formed into anarc, the vertex of which is a point of application R of the componentforce, and the radius of which is 100 to 200 mm, the engaging positioncan be made constant.

As illustrated in FIG. 8, in the hydraulic fluid supply pipe 25, inorder to supply hydraulic fluid to the first hydraulic cylinder 22,pressure regulating valves 39, 40 for regulating the pressure of fluidsupplied from the hydraulic fluid supply primary pipe 38 at apredetermined value, an electromagnetic changeover valve 41 for changingover the hydraulic fluid supply pipe line, and a supply pipe 42 forsupplying hydraulic fluid, are connected with the piston rod 22b of thehydraulic cylinder 22. Also, in order to supply hydraulic fluid to thesecond hydraulic cylinder 23, pressure regulating valves 43, 44 forregulating the pressure of fluid supplied from the hydraulic fluidsupply primary pipe 38 at a predetermined value, an electromagneticchangeover valve 45 for changing over the hydraulic fluid supply pipeline, and a supply pipe 46 for supplying hydraulic fluid, are connectedwith the piston rod 23b of the hydraulic cylinder 23.

It is necessary to use a flexible tube for a portion of the supply pipes42, 46 so that the piston rods 22b, 23b can be smoothly reciprocated.

Instead of the above hydraulic cylinders 22, 23, it is possible to use ahydraulic cylinder constructed in such a manner that hydraulic fluid issupplied to the cylinder bodies 22a, 23a.

In accordance with an operation signal sent from the control unit 9, theelectromagnetic changeover valves 41, 45 are activated, so thathydraulic fluid of high or low pressure can be supplied to the hydrauliccylinders 22, 23.

As illustrated in FIG. 9, in the hydraulic fluid supply pipe 25, thepressure regulating valve 40 of the first cylinder 22 may be commonlyused, and hydraulic fluid may be supplied to the second hydrauliccylinder 23 through the supply pipe 47.

Further, as illustrated in FIG. 10, in the hydraulic fluid supply pipe25, instead of the pressure regulating valves 39, 40, 43, 44,electric-pneumatic converters 48, 49 may be used, by which hydraulicpressure is arbitrarily adjusted in accordance with an electric signalsent from the control unit 9, so that hydraulic fluid can be supplied tothe hydraulic cylinders 22, 23 through the supply pipes 50, 51.According to this construction, the electromagnetic changeover valves41, 45 can be omitted, and further the surface pressure of the pressureroller 5 can be accurately controlled.

In the yarn winder described above, the slider 12 and frame body 13 aresupported by the hydraulic cylinders 22, 23 under the condition thatboth ends are held. Therefore, moment is seldom applied to the slidingball bearing 21.

However, in the case where moment is seldom applied to the sliding ballbearing 21, the running resistance of the sliding ball bearing 21 isgreatly reduced. As a result, vibration tends to occur in the slidingball bearing 21.

In order to solve the above problem, when the hydraulic cylinders 22,23, the inner diameters of which are different, are provided so thatdifferent supporting forces can be applied to the frame body 13, amoment to prevent the occurrence of vibration is generated and given tothe sliding ball bearing 21.

In this connection, in the case where the frequency of vibrationgenerated by the rotation of the spindle 2 during the yarn windingoperation, coincides with the natural frequency of a portion includingthe slider 12, frame body 13, sliding ball bearing 21 and hydrauliccylinders 22, 23, the operation is carried out in the following manner:Pressures of hydraulic fluid supplied to the hydraulic cylinders 22, 23are respectively regulated by the pressure regulating valves 39, 40, 43,44 provided in the hydraulic fluid supply pipe 25. In accordance with asignal sent from the vibration detector 26, the pipe lines of theelectromagnetic valves 41, 45 are switched, so that the pressuressupplied to the hydraulic cylinders 22, 23 are changed.

Alternatively, the following construction may be employed:

The above vibration detector 26 is not provided. In the control unit 9,the time at which the frequency of vibration generated by the rotationof the spindle coincides with the natural frequency, is calculated inaccordance with the winding condition. When the yarn winding time iscoincident with the previously calculated time, the pipe lines of theelectromagnetic changeover valves 41, 45 are switched.

Alternatively, the following construction may be employed: A rotationalspeed of the spindle is previously monitored, at which the frequency ofvibration generated by the rotation of the spindle coincides with thenatural frequency. The monitored rotational speed is previously inputtedinto the control unit 9. The rotational speed of the spindle is detectedduring the yarn winding operation. When the detected rotational speedcoincides with the previously inputted rotational speed, the pipe linesof the electromagnetic changeover valves 41, 45 are switched.

In the case where it is not necessary to accurately control the surfacepressure of the pressure roller 5, only the pressure of hydraulic fluidsupplied to the hydraulic cylinder 22 is changed in the hydraulic fluidsupply pipe 25 shown in FIG. 9.

When the hydraulic fluid supply pipe 25 having electric-pneumaticconverters 48, 49 is used as illustrated in FIG. 10, the contactpressure of the pressure roller 5 can be arbitrarily controlled duringthe yarn winding operation.

When throttle valves are provided in the supply pipes 42, 46, 47, 50, 51for supplying hydraulic fluid to the hydraulic cylinders 22, 23 so thatthe amount of hydraulic fluid discharged from the hydraulic cylinders22, 23 can be changed, a damping effect can be provided.

As shown in FIG. 26, the throttle valves can also be provided on thehydraulic fluid supply pipe arranged between the electromagneticchangeover valve and the pressure regulating valve.

In this case, since the throttle valve is switched simultaneously withthe changeover operation of the pressure, a suitable damping effect canbe obtained, in response to the pressure applied to this pipe.

When hydraulic-pneumatic converter are provided instead of the throttlevalves described above so that hydraulic fluid can be supplied to thehydraulic cylinders 22, 23, damping effect can be provided moreeffectively.

In the above winder, the moment M0 applied to the sliding ball bearing21 can be calculated by the following expression.

    M0=L×W-L2×W2

where the load activated at the center of gravity of the frame body 13is W; the distance from the center of gravity G to the center of theguide 1a is L; the inclination angle formed between a tangential lineand a vertical straight line is θ, wherein the tangential line is formedbetween the stopper member 33 of the stopper means 24 and the contactsurface of the engaging member 36; the reaction force on the contactsurface, which is directed upward in the vertical direction, is W1; thecomponent force activated on the contact surface making a right angle isW2; and the distance from the point of application R of the componentforce W2 to the point of intersection P formed by the extension line ofthe tangential line and the vertical line of the guide 1a, is L2.

The component force W2 in the above expression is expressed as follows.

    W2=W1/sin θ

In the above winder, the moment M0 applied to the sliding ball bearing21 is expressed as follows.

    M0=100×200-15×1/sin 10°×200=2723 Kg·cm

where the load is 200 Kg; the distance L from the center of gravity G tothe center of the guide 1a is 100 cm; the inclination angle θ is 10°;and the distance L2 from the point of application R of the componentforce W2 to the point of intersection P formed by the extension line ofthe tangential line and the vertical line of the guide 1a, is 15 cm.

As can be seen from the above expressions, compared with a case shown inFIG. 18 in which the conventional stopper means is used, the momentapplied to the sliding ball bearing 21 can be greatly reduced in thiscase. Therefore, a compact sliding ball bearing, the allowable moment ofwhich is low, can be used.

Of course, the yarn winder of the present invention can be applied tothe winder shown in FIG. 1 in which one spindle is provided.

Next, the construction of the pressure roller 5 shown in FIG. 1 will beexplained as follows.

FIG. 11 is a sectional view showing an outline of one example of thepressure roller 5. In the pressure roller 5, the electric motor 6 fordriving is integrally provided at an end portion of the roller 60. Theshaft portion 60b protruded from an end portion of the roller body 60aof the roller 60 is rotatably attached to the bracket 61 through thebearing 62. At the other end portion of the roller 60a, the shaftportion 60c is protruded, and the rotor 63 is mounted on the protrudedshaft portion 60c. The end of the shaft portion 60c is rotatablysupported by the housing 65 through the bearing 66, wherein the housingsupports the stator 64 disposed in such a manner that the stator 64covers the rotor 63.

The housing 65 described above is of the integrated type or the splittype, and attached to the frame body 13.

In order to prevent an increase in the temperature of the housing 65, aplurality of heat pipes 67 are provided in the outer periphery of thestator mounting portion in the circumferential direction (shown in FIG.14) in such a manner that end portions of the heat pipes 67 protrudefrom the housing 65, and fins 68 for cooling are mounted on theprotruding portions of the heat pipes 67.

Instead of the aforementioned fins 68, a jacket in which fluid forcooling is circulated, or a jacket in which fluid for cooling isenclosed may be attached.

In the pressure roller 5 explained above, when the housing 65 is heatedby the heat generated in the electric motor 6 section for driving, thegenerated heat is transmitted to the fins 68 of low temperature throughthe heat pipes 67 inserted into the housing 65. Therefore, the heat isradiated from the surfaces of the fin 68, and at the same time the heatis also radiated from the peripheral surface of the housing 65.

As described above, the heat in the housing 65 is transmitted to thefins 68 through the heat pipes 67 and radiated. Accordingly, thetemperature of the bearing 66 of the electric motor 6 for driving is notabnormally raised, so that the lubricant in the bearing is notdeteriorated, and it possible to prevent the life of the bearing frombeing reduced. When the operation was carried out under the conditionthat the yarn winding speed was set at 4000 m/min, the increase intemperature of the bearing portion was reduced by about 20° C. While thebearing of the conventional pressure roller mechanism was replaced whenit was operated for about 10000 hours, the bearing of the pressureroller mechanism of the present invention was replaced when it wasoperated for about 19000 hours which was approximately twice as long.

When the bearing 66 was lubricated by compressed air containinglubricating oil and the yarn winding speed was set at 7000 m/min, thetemperature of the roller body 60a was lowered from (the roomtemperature+19° C.) to (the room temperature+11° C.), and thedeterioration of yarn quality, to be caused when the shaft portion 60cand roller body 60a were heated by the heat generated by the electricmotor 6 for driving, was prevented.

When one set of electric motor 6 for driving is installed in the endportion of the roller 60, as illustrated in FIG. 12, the shaft portion60d is formed in such a manner that an annular gap portion 60e isprovided at the end of the roller body 60a, and at the same time, thestator mounting portion 69a for the stator 64 of the housing 69 isformed into a cylindrical shape, so that the mounting portion 69a can bepositioned in the annular gap portion 60e of the roller 60.

When the electric motor 6 for driving is disposed in the end portion ofthe roller 60 as described above, the length of the pressure roller 5can be reduced in the axial direction.

In the case where the electric motors 6 for driving are disposed at bothend portions of the roller 60 wherein one electric motor is disposed ateach end, as illustrated in FIG. 13, the shaft portion 60d is formed insuch a manner that annular gap portions 60e are provided at both ends ofthe roller body 60a, and at the same time, in each end portion, thestator mounting portion 69a for the stator 64 of the housing 69 isformed into a cylindrical shape, so that the mounting portion 69a can bepositioned in the annular gap portion 60e of the roller 60.

When the electric motors 6 for driving are disposed at both end portionsof the roller 60, the size of the individual motors can be furtherreduced, and the diameter of the roller 60 can be reduced.

When the pressure roller 5 is of the drive roller type and a heatconductive member is provided in the roller, as illustrated in FIG. 15,the drive motor 6 for driving is integrally attached to the end portionof the roller 60. One shaft portion 60b of the roller 60 is rotatablysupported by the frame body 13 through the bearing, and the other shaftportion 60c is extended and provided with the rotor 63. The end of theshaft portion 60c is rotatably supported by the housing 65 through thebearing 66, wherein the housing supports the stator 64 disposed in sucha manner that the stator 64 covers the rotor 63.

A hole is formed in the axis portion of the roller 60, and a heat pipe70 is inserted into the hole in such a manner that one end of the heatpipe 70 is positioned at the end of the roller body 60a or the bearingportion 60 of the shaft portion 60b, and the other end of the heat pipe70 is positioned at the bearing portion 66 of the shaft portion 60c. Inorder to prevent the movement of the heat pipe 70, a blank cap 71 isscrewed to the end portion of the shaft 60c.

The above housing 65 is of the integrated type or the split type. Thehousing 65 is mounted on the frame body 13 of the traverse unit 4, and aplurality of heat pipes 67 are inserted into the housing 65 in the outercircumferential direction in the same manner as that shown in FIG. 11.Fins 68 are mounted at the protruding portions of the heat pipes 67.

It is possible to employ the construction in which the shaft portion 60cof the roller 60 is extended and connected with the output shaft of aninduction motor available in the market, wherein the rotor 63 forelectric motor use is not attached to the shaft portion 60c. In thisconstruction, a piece of heat conductive member is inserted into theaxis portion of the rotational shaft of the induction motor in such amanner that the heat conductive member penetrates the axis portion. Atthe same time, it is also necessary to insert a heat conductive memberinto the housing portion for supporting the stator of the inductionmotor in such a manner that an end portion of the heat conductive memberprotrudes from the housing so as to attach a cooling member to theprotruding portion.

In the drive type pressure roller 5 explained above, when the housing 65is heated by the heat generated in the electric motor 66 section fordriving, the generated heat is transmitted to the fins 68 at a lowtemperature through the heat pipes 67 inserted into the housing 65.Therefore, the heat is radiated from the surfaces of the fins 68, and atthe same time the heat is also radiated from the peripheral surface ofthe housing 65.

On the other hand, when the shaft portion 60c of the roller 60 isheated, the generated heat is transmitted to the roller body 60a, thetemperature of which is low, by the action of the heat pipe 60 insertedinto the roller 60, and the transmitted heat is radiated from the entirecircumferential surface of the roller body 60a.

As described above, the heat in the housing 65 is transmitted to thefins 68 through the heat pipes 67 and radiated, and at the same time,the heat of the shaft portion 60c is transmitted to the roller body 60aby the action of the heat pipe 70, and the transmitted heat is radiatedfrom the entire circumferential surface. Accordingly, the temperature ofthe bearing 66 of the electric motor 6 for driving is not abnormallyraised, so that the lubricant in the bearing is not deteriorated, and itpossible to prevent the life of the bearing from being reduced. When theoperation was carried out under the condition that the yarn windingspeed was set at 5000 m/min, the increase in temperature of the bearingportion was reduced by about 20° C. While the bearing of theconventional pressure roller mechanism was replaced when it was operatedfor about 10000 hours, the bearing of the pressure roller mechanism ofthe present invention was replaced when it was operated for about 19000hours which was approximately twice as long.

In the examples explained above, the shaft portion of the pressureroller is rotated. However, the present invention can be applied to anouter rotor type pressure roller in which the shaft is fixed to thehousing.

In the case where the pressure roller 5 is an idle type roller rotatedby a package and a heat conductive member is inserted into the pressureroller 5, as illustrated in FIG. 16, the pressure roller 5 includes: aroller 60, the shaft portions 60b of which are protruded from both sidesof the roller body 60a; a heat pipe 70 inserted into a hole formed inthe axial portion of the roller 60; blank caps 71 screwed to the endportion of the heat pipe 70; and bearings for supporting both shaftportions 60b of the roller 60.

Instead of the heat pipe described above, a heat conductive member madeof copper alloy having a high thermal conductivity may be used.

The aforementioned bearing is composed of a bearing 62 rotatablysupporting the bearing portion 60b of the roller 60, and a bracket 61supporting the bearing 62.

When the roller 60 is rotated by a tube tightly provided around thespindle 2 or rotated by a package, the bearing 62 is heated, so that thebracket 61 coming into contact with the outer race portion of thebearing 62 is also heated. Then the bearing 62 is cooled when thegenerated heat is radiated from the peripheral surface of the bracket61.

On the other hand, the shaft portion 60b of the roller 60 coming intocontact with the inner race portion of the bearing 62 is heated, theheat is transmitted to the roller body 60a side of low temperature, andthe heat is radiated from the entire surface of the roller body 60a, sothat the bearing 62 is cooled.

In the above roller 60, the generated heat of the shaft portion 60b istransmitted to the entire roller body 60a. Therefore, the radiationefficiency is greatly improved. As a result, the temperature of thebearing 62 is not increased, and the deterioration of lubricant can beavoided, so that the deterioration of bearing life can be prevented.When the yarn winding operation was conducted under the condition thatthe yarn winding speed was set at 5000 m/min, the increase in bearingtemperature was reduced by not less than 20° C. Therefore, the bearinglife was increased to 20000 hours which was approximately 1.5 times aslong as the bearing life 13000 hours of the conventional pressureroller.

Even when the bearing portion 60b of the roller 60 was heated by theheat generated in the bearing 62 and the temperature of the bearingportion 60b was raised, the generated heat was immediately transmittedby the heat pipe 70 to a portion of low temperature. Accordingly, notonly the temperature of the end portion of the roller body 60a close tothe shaft portion 60b but also the temperature of the entire roller body60a was made to be approximately uniform. In the conventional pressureroller, a temperature difference between the end and center of a yarncontact portion was approximately 5 to 10° C., however, it wasmaintained to be not more than 1° C. all over the yarn contact portionin this example.

In the above example, the heat pipe 70, which was a heat conductivemember, was inserted into the roller 60 all over its length, however,the approximately same effect can be provided when a heat pipe isinserted, the length of which covers the bearing and the heat generatingportion of the electric motor for driving.

The sequential operations of the controlling method for controlling aturret type yarn winder which is one of embodiments of the presentinvention, will be explained with reference to FIGS. 22 to 25,hereunder.

After starting, at the step 1, power and compressed air are supplied tothis controlling system and the system is started.

In step 2, yarn-winding conditions suitable for a specific yarn used tobe wound on a tube is predeterminedly set.

Thereafter, in step 3, a first switch S1 is turned ON to therebygenerate a command for starting the yarn winding operation and in step4, the hydraulic fluid cylinder 35 is actuated and thus in step 5, thestopper member 33 is raised to move to a waiting position.

Then, in step 6, a switching operation is carried out to introducecompressed air into the hydraulic fluid cylinder 22 and 23 and in step7, the frame body 13 is descended.

In step 8, another hydraulic fluid cylinder 18 is actuatedsimultaneously with the descending of the frame body 13, so that apiston thereof is projected and thus in step 9, the descending distanceof the frame body 13 is limited and therefore, a predetermined distanceL can be created between the pressure roller 5 and the empty tube 100.

Thereafter, in step 10, a second switch S2 is turned ON and therefore,in step 11, motors for driving the spindle 2, the traverse unit 4 andthe pressure roller 5 are actuated to thereby rotate the spindle 2, thetraverse unit 4 and the pressure roller 5 respectively, in accordancewith the yarn-winding condition which is set in step 2.

In step 12, it is determined whether or not the acceleration of themotors is completed, and if the answer is NO, then go back to thestarting point of this step 12 and the same operation will be repeated,on the other hand, if the answer is YES, then go to step 13, and thecalculation for determining the slippage of the pressure roller, will becarried out.

Then, in step 14, the rotation of the pressure roller 5 is adjustedutilizing the slippage information, and in step 15, the preparations forintroducing the yarn into the yarn winder and for yarn taking operation,are carried out.

Thereafter, in step 16, a third switch S3 is turned ON, and in step 17,the yarn taking up operation is started and in step 18, the yarn-windingoperation is started.

Next, in step 19, the calculation for determining a diameter of the yarnlayer 220 formed on the tube 100 is carried out.

The calculation for determining a diameter D of the yarn layer iscarried out utilizing a conventional method and, for example, it maycarried out by utilizing the following calculation formula: ##EQU17##where, D denotes a diameter (cm) of the yarn layer: D₀ denotes anexternal diameter of a tube (cm):

St denotes yarn winding width on the tube (cm) (transverse to a strokedirection):

ρ denotes a yarn concentration on the tube (gcm³):

T denotes yarn winding period (min) (elapsed time from the starting timefor yarn winding operation):

Tp denotes an output value of the yarn output from a yarn supplyingmeans (g/min) (through put value):

Then, in step 20, the rotation of the spindle is obtained bycalculation. The calculation to obtain the rotation speed of the spindleVsp can be carried out by utilizing a conventional method or utilizingthe following calculation formula: ##EQU18## where, Vsp denotes therotation speed of the spindle: V denotes the yarn winding speed (m/min):and

D1 denotes a diameter (cm) of the yarn layer:

Thereafter, in step 21, the adjustment operation is carried out in whichthe rotation speed of the spindle is adjusted with respect to theslippage information, and in step 22, the current diameter of the yarnlayer is compared with the predeterminedly set value for the diameter todetermine whether or not the current diameter thereof exceeds thepredeterminedly set value.

If the answer is NO, then go to step 19, and all of the above-mentionedsteps are repeated, while if the answer is YES, then go to step 23.

In step 23, the hydraulic fluid cylinder 18 is actuated to have thepiston thereof, holding the frame body 13 at a predetermined position,withdrawn.

Therefore, in step 24, the pressure roller 5 can bring into contact witha surface of thin layered yarns 220 wound on the surface of the tube100.

In the present invention, above-mentioned steps 19 to 24 are called asfeed-forward control.

Thereafter, in step 25, the rotation number of the pressure roller 5 isdetected an in step 26, the adjustment for the rotation of the spindleis carried out.

Then, in step 27 it is determined whether or not a yarn switching switchS4 is turned ON, and if the answer is NO, then in step 28, the currentwinding time is compared with a predeterminedly set yarn winding timeand it is determined whether or not the current yarn winding timeexceeds the predeterminedly set value. And if the answer is YES, then goback to step 25, and all of the above-mentioned operations are repeatedand if the answer is NO, then go to step 29. In step 29, it isdetermined whether or not the yarn winding operation is completed and ifthe answer is YES, then go to END to stop the yarn-winding operation,but if the answer is NO, then go to step 30 to start the rotation of thewaiting spindle.

On the other hand, in step 27, the answer is YES, then go to step 30 byskipping the steps 27 and 28.

Then, in step 31, it is determined whether or not the acceleration ofthe motor for rotate the spindle is completed, and if the answer is NO,then go to the operation of this step 31 is repeated while the answer isYES, then go to step 32 and yarn switching operation is carried out.

In the step 32, the rotating speed of the pressure roller 5 in the yarnswitching operation, is preferably increased in accordance with therotational speed of the fully loaded tube before the yarn switchingoperation is completed.

On the other hand, the rotating speed of the pressure roller 5 ispreferably switched up to a period when the yarn switching operation iscompleted, so that the rotating speed of the pressure roller 5 isapproximately identical to the empty tube which should be changed fornext yarn winding operation.

Thereafter, in step 33, the slippage of the pressure roller 5 iscalculated and in step 34, the rotating speed of the pressure roller 5is adjusted with respect to the slippage information.

Then, the winding tube switching operation is carried out and go back tostep 19 and all of the above-mentioned operation indicated in thefollowing steps are sequentially repeated.

As described in the first aspect of the present invention, the presentinvention is to provide a method for controlling the drive of a yarnwinder in which a yarn is wound by a spindle drive type winder having apositively driven pressure roller, the method comprising the steps of:positioning the pressure roller so that the pressure roller is notcontacted with a tube immediately after the yarn switching operationwhen the yarn is switched from the fully loaded tube to the empty tube;moving at least one of the pressure roller and the tube in a directionso that a distance between the pressure roller and the tube is reducedafter a predetermined amount of yarn layer has been formed on the tube;permitting the pressure roller to come into contact with the yarn layerprovided on the tube at a predetermined surface pressure; controllingthe surface speed of the pressure roller to be higher than that of theempty tube until the yarn is switched to the empty tube side, whereinthe controlled speed is approximately the same as or lower than thesurface speed of the fully loaded tube; and controlling the surfacespeed of the pressure roller to be approximately the same as the surfacespeed of the empty tube after the yarn has been switched to the emptytube. Accordingly, in the yarn switching operation, an unnecessarytension fluctuation is not caused, and the yarn can be stably switched.When the speed of the pressure roller is switched at least before theyarn starts traversing, a package, the characteristics of which areuniform from the most inner layer to the most outer layer, can beprovided.

As described in the second aspect of the present invention, the presentinvention is to provide a method for controlling the drive of a yarnwinder in which a yarn is wound by a spindle drive type winder having apositively driven pressure roller, the method comprising the steps of:positioning the pressure roller so that the pressure roller is notcontacted with a tube immediately after the yarn setting operation orthe yarn switching operation; moving at least one of the pressure rollerand the tube in a direction so that a distance between the pressureroller and the tube is reduced after a predetermined amount of yarnlayer has been formed on the tube; permitting the pressure roller tocome into contact with the yarn layer provided on the tube at apredetermined surface pressure; and switching the rotational speedcontrol of the spindle from feed forward control based on thecalculation of winding diameter, to feedback control by which therotational speed of the spindle is controlled to a predetermined windingspeed based on the rotational speed of the pressure roller when thepressure roller comes into contact with the yarn layer formed on thetube. Therefore, the rotational speed control of the spindle can beswitched under the condition that the pressure roller comes into contactwith a yarn layer on the tube with a predetermined surface pressure.Consequently, switching time of the rotational control of the spindlecan be made to be constant, and accurate speed control can be carriedout.

As described in the third aspect of the present invention, the presentinvention is to provide a method for controlling the drive of thepressure roller of a yarn winder in which a yarn is wound by a spindledrive type winder having an electric motor for driving the pressureroller, comprising the steps of: rotating the pressure roller by theelectric motor at the yarn setting operation or the yarn switchingoperation under the condition that the pressure roller is not contactedwith a tube tightly attached to the spindle; calculating a slippagecaused in the electric motor; and correcting a command frequency givento the electric motor so as to command the rotation of the electricmotor in accordance with the slippage. Accordingly, even after thewinder, electric motor and bearing have been replaced, the slippage canbe automatically calculated and renewed in the yarn setting operation inwhich the yarn winding starts, or in the yarn switching operation. Afterthe calculation, the yarn winding operation can be carried out under apredetermined condition, so that a package of uniform configuration canbe provided.

Also, the occurrence of heat generation and damage of the electric motorcaused by overload can be prevented. Further, measurement of slippage ofthe electric motor for driving the pressure roller can be omitted at thetime of completion of assembling the winder and also at the time ofcompletion of replacing the bearing.

Also, according to the fourth aspect of the present invention, thepresent invention is to provide a method for controlling the drive ofthe pressure roller of a yarn winder, further comprising the step ofcalculating the slippage caused in the electric motor for driving thepressure roller by the number of pressure roller rotation detectingpulses or the number of detected rotation when the pressure roller isrotated by the electric motor at a predetermined rotational speed, andalso calculating by the number of pulses or the number of rotation foundwhile the slippage of the electric motor is neglected. Alternatively,according to the fifth aspect thereof, the present invention is toprovide a method for controlling the drive of the pressure roller of ayarn winder, further comprising the step of calculating the slippagecaused in the electric motor for driving the pressure roller by acommand frequency at the time when the pressure roller is rotated by theelectric motor at a predetermined speed, and also calculated by afrequency found while the slippage is neglected. Therefore, it is notnecessary to install a specific apparatus for measuring the slippage,and it is possible to find an accurate slippage using only the existingapparatus.

According to the sixth aspect thereof, the present invention is toprovide a yarn winder comprising hydraulic cylinders provided at bothend portions of the frame body, wherein both end portions of the framebody are supported by the two hydraulic cylinders. Therefore, therunning resistance of the sliding ball bearing can be reduced, and thesurface pressure control of the pressure roller can be accuratelycarried out. Since the sliding ball bearing is not given a high moment,a sliding ball bearing, the allowable moment of which is low, can beapplied, so that the diameter and length of the sliding ball bearing canbe reduced. As a result, the overall height of the winder can belowered.

According to the seventh aspect thereof, it is possible to adopt theconstruction in which the inner diameters of the two hydraulic cylindersare different. When the above construction is adopted, the winder can becontrolled so that vibration is not caused during the winding operation.

According to the eighth aspect thereof, the present invention is toprovide a yarn winder, in which a hydraulic fluid supply pipe isconnected to each hydraulic cylinder, and a control unit is provided anda pipe line of the hydraulic fluid supply pipe is changed or hydraulicpressure of the supplied fluid is controlled in accordance with a signalsent from the control unit. Therefore, when resonance is caused duringthe winding operation, the resonance is accurately detected, andhydraulic pressure of each hydraulic cylinder is changed so that amoment activated on the sliding ball bearing is changed. In this way,damping resistance force can be adjusted, and resonance can be quicklyavoided.

According to ninth aspect thereof, the present invention is to provide ayarn winder, comprising a stopper means for fixing the frame body to themachine frame so that the pressure roller is not contacted with thetubes held by the spindle, the stopper means including a stopper memberprovided on the machine frame side and an engaging member provided inthe frame body, wherein a contact surface of the stopper and engagingmembers is inclined by and angle of 0° to 45° so that a lower tangentialline of the contact surface is inclined toward the cantilever supportingside of a movable frame body. Therefore, since the sliding ball bearingis not given a high moment when the frame body is held by the stoppermeans, a sliding ball bearing, the allowable moment of which is low, canbe applied, so that the diameter and length of the sliding ball bearingcan be reduced. As a result, the overall height of the winder can belowered.

According to the tenth aspect thereof, the pressure roller of the yarnwinder comprises an electric motor provided at one end portion of thepressure roller, wherein a shaft of the pressure roller and an outputshaft of the electric motor are commonly used, and according to theeleventh aspect thereof, the pressure roller of the yarn windercomprises electric motors provided at both end portions of the pressureroller, wherein a shaft of the pressure roller and an output shaft ofthe electric motor are commonly used. Therefore, it is possible to makethe pressure roller compact and light, and further it is possible tomake the sizes of individual motors small.

According to twelfth aspect thereof, the present invention is to providea pressure roller of the yarn winder comprising an electric motorprovided at one end portion of the pressure roller, wherein a shaft ofthe pressure roller and an output shaft of the electric motor arecommonly used, and a heat conductive member is inserted into a housingportion of the electric motor in such a manner that the heat conductivemember is protruded onto the opposite side to the pressure roller and acooling member is attached to the protruding portion of the heatconductive member. Therefore, the heat generated in the electric motorportion can be quickly radiated, and it is possible to prevent thebearing life from being reduced due to the heat generated in theelectric motor portion. Further, it is possible to prevent the rollerbody from being heated so that a change in the characteristics of theyarn coming into contact with the roller body can be avoided.

According to other embodiment of the twelfth aspect thereof, the presentinvention is to provide a pressure roller of the yarn winder in which aheat conductive member is inserted into a core portion of the pressureroller in the longitudinal direction of the core including at least thehousing portion of the electric motor. According to another embodimentof this aspect, the present invention is to provide a pressure roller ofthe yarn winder in which the pressure roller is rotatably attached to asupporting member through a bearing, and a heat conductive member isinserted into the pressure roller in the longitudinal direction of thecore of the pressure roller including at least bearing portions providedat both ends. Therefore, the heat generated in the bearing portion canbe transmitted by the heat conductive member to a portion of the roller,the temperature of which is low. Consequently, it is possible to preventthe bearing life from being shortened, and the occurrence of uneventemperature distribution on the roller can be eliminated.

We claim:
 1. A winding machine for winding a yarn from a yarn supplyingsource, comprising:a machine frame; a spindle rotatably attached to themachine frame, said spindle supporting a plurality of tubes on whichyarns are wound; a pressure roller movable into contact with a yarnlayer wound around the tubes supported by the spindle; a traverse unitprovided upstream, in terms of yarn travel to the tubes, from thepressure roller; a frame body having opposite end portions and rotatablysupporting the pressure roller, the frame body being slidably supportedat one of said opposite end portions, for movement normal to a directionbetween the opposite end portions, by and cantilevered from the machineframe for advancement of the pressure roller toward and retractionthereof from the spindle; and at least two actuating cylinders, providedone at each of said opposite end portions of the frame body, forobtaining the movement of the frame body relative to the machine frame,said end portions of the frame body being located adjacent to oppositeaxial ends of the pressure roller, respectively.
 2. A yarn winderaccording to claim 1, wherein the inner diameters of each one of said atleast two actuating cylinders are different from each other.
 3. A yarnwinder according to claim 1, wherein each of said actuating cylindersare connected to a respective actuating fluid supply pipe, and includingcontrol means for controlling actuating fluid flowing through each saidactuating fluid supply pipe, wherein pressure of said actuating fluidflowing through each of said actuating fluid supply pipes is adjustedwith respect to a controlling signal output from said control means. 4.A yarn winder according to claim 3, wherein said actuating fluid pipecomprises a plurality of sub actuating fluid pipes, each of said subactuating fluid pipes being connected to the respective actuatingcylinder and supplying the actuating fluid under pressure different fromthat supplied by the other actuating cylinder, and wherein said controlmeans selects one of said actuating fluid supply pipes and saidactuating cylinder connected thereto and supplies actuating fluid undera predetermined pressure.
 5. A yarn winder according to claim 1,including at least one pressure adjusting means for adjusting pressureof said actuating fluid and provided on said actuating fluid supply pipeconnected to said actuating cylinder, and wherein said control meansselectively controls said pressure adjusting means so that actuatingfluid is supplied to said actuating cylinder under a predeterminedpressure.